US7165889B2 - Bearing oil lift pocket - Google Patents
Bearing oil lift pocket Download PDFInfo
- Publication number
- US7165889B2 US7165889B2 US11/044,792 US4479205A US7165889B2 US 7165889 B2 US7165889 B2 US 7165889B2 US 4479205 A US4479205 A US 4479205A US 7165889 B2 US7165889 B2 US 7165889B2
- Authority
- US
- United States
- Prior art keywords
- channel
- supply port
- bend
- longitudinal axis
- lift pocket
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related, expires
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0685—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C39/00—Relieving load on bearings
- F16C39/04—Relieving load on bearings using hydraulic or pneumatic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/10—Application independent of particular apparatuses related to size
- F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
Definitions
- This invention is directed generally to bearings and, more particularly, to oil lift pockets in bearing assemblies.
- Oil pockets of various descriptions have been used on bearing surfaces, such as babbitts, to reduce friction associated with shafts in contact with the bearing surfaces with varying degrees of success.
- oil lift pockets have been used to reduce friction. Friction is reduced by injecting oil under high pressure, such as greater than about 500 psi, to reduce the load of the shaft on the bearing surface and thereby reduce the friction of the shaft on the bearing surface.
- Conventional configurations of oil lift pockets have reduced friction found in such configurations.
- use of such oil lift pockets has resulted in delamination of the babbitt and dead zones in which dirt and other contaminants have accumulated.
- This invention relates to an oil lift pocket for a bearing assembly for reducing friction between a shaft or other element and a bearing surface.
- Oil may be injected under a pressure of between about 1,800 pounds per square inch (psi) and about 2,200 psig and at a flow rate of between about one gallon per minute and about four gallons per minute into the oil lift pocket. Injection of the oil may reduce friction, thereby reducing breakaway torque between about 60 fold and about 200 fold.
- Reduction of friction using the oil lift pocket enables smaller, lower cost turning motors to be used without requiring that other components be changed.
- the reduced friction equates to reduced breakaway torque associated with initial rotation of a shaft.
- the reduced friction also enables higher projected pad pressures to be used than conventional systems, thereby enabling smaller, more efficient bearings to be used during slow speed operations.
- the oil lift pocket may include a cylindrical bearing surface and a supply port extending through the cylindrical bearing surface.
- the oil pocket may also include a plurality of channels extending from the supply port.
- the oil lift pocket may include first, second, third, and fourth channels extending from the supply port forming a bowtie shaped oil lift pocket without the channels contacting each other at the tips of the channels.
- the first channel may extend from the supply port and have a bend between a first end of the first channel and a second end of the first channel, wherein the second end of the first channel is in communication with the supply port.
- the oil lift pocket may also include a second channel extending from the supply port and having a bend between a first end of the second channel and a second end of the second channel such that the first end of the second channel terminates proximate to the first end of the first channel, wherein the second end of the second channel is in communication with the supply port.
- the oil lift pocket may include a third channel extending from the supply port and having a bend between a first end of the third channel and a second end of the third channel, wherein the second end of the third channel is in communication with the supply port.
- the oil lift pocket may include a fourth channel extending from the supply port and having a bend between a first end of the fourth channel and a second end of the fourth channel such that the first end of the fourth channel terminates proximate to the first end of the third channel, wherein the second end of the fourth channel is in communication with the supply port.
- Each of the channels may be formed from a first section and a second section, which may be divided by the bends in each channel.
- the sections of the channels may extend from the supply port at an angle relative to a longitudinal axis.
- the size of the angles between the sections of the channels and the longitudinal axis may vary or be the same. In at least one embodiment, each of the angles is the same.
- An advantage of the oil lift pocket of this invention is that the coefficient of friction may be reduced between about 60 fold and about 200 fold, and the breakaway torque may be reduced as well.
- Another advantage of this invention is that the reduction of the coefficient of friction enables smaller, lower cost turning motors to be used.
- Yet another advantage of this invention is that the oil lift pocket allows for higher projected pad pressures to be used, which enables smaller, more efficient bearings to be used.
- Still another advantage of this invention is that the oil lift pocket eliminates dead zones for contaminant accumulation, babbitt delamination, and nonuniform support and lift.
- FIG. 1 is a perspective view of an oil lift pocket system of the instant invention installed in a turbine engine.
- FIG. 2 is a frontal view of the oil lift pocket system shown in FIG. 1 on an inner surface of a rotor.
- this invention is directed to an oil lift pocket 10 for reducing friction in relatively slow turning applications, such as when a shaft 12 is rotating at speeds less than about 400 revolutions per minute (rpm).
- the oil lift pocket 10 of this invention may be capable of reducing friction, as quantified by the coefficient of friction, between 60 and 200 fold. Such a large reduction in friction enables smaller sized turning motors to be used in the same application and smaller, more efficient bearings to be used, resulting in increased efficiency.
- the oil lift pocket 10 may be formed on a bearing surface 14 .
- the bearing surface 14 may be, but is not limited to being, a babbitt or other appropriate structure, and may be formed from any appropriate material.
- the bearing surface 14 may include a plurality of oil channels 16 for containing pressurized oil for reducing friction on a shaft. More specifically, the bearing surface 14 may include channels 16 extending from a supply port 18 in a configuration that resembles a bowtie. However, in at least one embodiment, the channels 16 extend from the supply port 18 but do not contact each other. Instead, the channels 16 may form a bowtie shape in which the channel do not contact each other.
- a first channel 20 may extend from the supply port 18 and have a bend 22 between a first end 24 of the first channel 20 and a second end 26 of the first channel 20 .
- the first channel 20 may be in fluid communication with the supply port 18 .
- a second channel 28 may extend from the supply port 18 and have a bend 30 between a first end 32 of the second channel 28 and a second end 34 of the second channel 28 .
- the second channel 28 may be in fluid communication with the supply port 18 .
- the bend 30 may be configured such that the first end 32 of the second channel 28 terminates proximate to the first end 24 of the first channel 20 while the bend 30 of the second channel 28 and the bend 30 of the first channel 20 are remote from each other, as shown in FIG. 2 .
- first and second channels 20 , 28 may, in at least one embodiment, be mirror images of each other.
- the oil lift pocket 10 may also include third and fourth channels 36 , 38 extending from the supply port 18 .
- the channels 36 , 38 may be in configuration that is a mirror image of the first and second channels 20 , 28 .
- the third channel 36 may extend from the supply port 18 and have a bend 40 between a first end 42 of the third channel 36 and a second end 44 of the first channel 20 .
- the third channel 20 may be in fluid communication with the supply port 18 to receive oil from the supply port 18 .
- the fourth channel 38 may extend from the supply port 18 and have a bend 46 between a first end 48 of the fourth channel 38 and a second end 50 of the fourth channel 38 .
- the fourth channel 38 may be in fluid communication with the supply port 18 .
- the bend 46 may be configured such that the first end 48 of the fourth channel 38 terminates proximate to the first end 42 of the third channel 36 while the bend 46 of the fourth channel 38 and the bend 40 of the third channel 36 are remote from each other, as shown in FIG. 2 . However, the bend 40 of the third channel 36 and the bend 46 of second channel 38 are positioned remotely from each other, forming one side of the bow tie configuration of the oil lift pocket 10 .
- the first and fourth channels 20 , 38 may extend from the supply port 18 generally opposite from each other.
- the second and third channels 28 , 36 may extend from the supply port 18 generally opposite from each other.
- the first, second, third, and fourth channels 20 , 28 , 36 , and 38 may extend from the supply port 18 at locations on the supply port that are generally equidistant from each other.
- the channels 16 may have portions of themselves that are positioned at angles relative to each other.
- the bend 22 in the first channel 20 may form a first section 52 proximate the first end 24 at a first angle 54 relative to a longitudinal axis 56
- the bend 30 in the second channel 28 may form a second section 58 proximate the second end 26 of the second channel 28 at the first angle 54 relative to the longitudinal axis 56 .
- the bend 30 in the second channel 28 may form a first section 60 proximate the first end 32 at a second angle 62 relative to the longitudinal axis 56
- the bend 22 in the first channel 20 may form a second section 64 proximate the second end 26 of the first channel 20 at the second angle 62 relative to the longitudinal axis 56
- the bend 40 in the third channel 36 may form a first section 66 proximate the first end 42 at a third angle 68 relative to the longitudinal axis 56
- the bend 46 in the fourth channel 38 may form a second section 70 proximate the second end 50 of the fourth channel 38 at the third angle 68 relative to the longitudinal axis 56 .
- the bend 46 in the fourth channel 38 may form a first section 72 proximate the first end 48 at a fourth angle 74 relative to the longitudinal axis 56
- the bend 40 in the third channel 36 forms a second section 76 proximate the second end 50 of the first channel 20 at the fourth angle 74 relative to the longitudinal axis 56
- the first, second, third, and fourth angles, 54 , 62 , 68 , and 74 may be different values, or one or more of the angles 54 , 62 , 68 , and 74 may have the same values.
- the first, second, third, and fourth angles, 54 , 62 , 68 , and 74 have the same values.
- the first, second, third, and fourth angles, 54 , 62 , 68 , and 74 may be between about 45 degrees and 60 degrees. Bearings having a relatively short length may have angles 54 , 62 , 68 , and 74 that are about 45 degrees, and bearings having a relatively long length may have angles 54 , 62 , 68 , and 74 that are about 60 degrees.
- the supply port 18 may have any appropriate configuration and be sized according to the anticipated flow rate of oil.
- a counterbore 78 may be positioned concentrically with the supply port 18 .
- the channels 20 , 28 , 36 , and 38 may have varying depths depending on the application. In at least one embodiment, the channels 20 , 28 , 36 , and 38 may have a depth of about 0.06 inches.
- oil is injected into the oil lift pocket 10 to reduce friction on a shaft in contact with the bearing surface 14 .
- oil is injected into the supply port 18 where the oil flows into the channels 16 .
- the oil may be injected under a pressure of between about 1,800 pounds per square inch (psi) and about 2,200 psig and at a flow rate of between about one gallon per minute and about four gallons per minute. Injection of the oil may reduce friction, thereby reducing breakaway torque by between about 60 and 200 fold.
- the configuration of the pocket does not contribute to the accumulation of contaminants.
Abstract
Description
Claims (18)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/044,792 US7165889B2 (en) | 2005-01-27 | 2005-01-27 | Bearing oil lift pocket |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/044,792 US7165889B2 (en) | 2005-01-27 | 2005-01-27 | Bearing oil lift pocket |
Publications (2)
Publication Number | Publication Date |
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US20060165326A1 US20060165326A1 (en) | 2006-07-27 |
US7165889B2 true US7165889B2 (en) | 2007-01-23 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/044,792 Expired - Fee Related US7165889B2 (en) | 2005-01-27 | 2005-01-27 | Bearing oil lift pocket |
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080107366A1 (en) * | 2006-11-06 | 2008-05-08 | Zippy Technology Corp. | Air fan bearing structure |
US20100054642A1 (en) * | 2008-08-26 | 2010-03-04 | Wolfgang Issler | Slide bearing |
US20120017735A1 (en) * | 2010-07-22 | 2012-01-26 | Makita Corporation | Cutting tools having movable cover mounting structures |
US8608385B2 (en) | 2011-05-18 | 2013-12-17 | Federal-Mogul Corporation | Main bearing for engine with high belt load |
US20140363307A1 (en) * | 2013-06-05 | 2014-12-11 | Siemens Aktiengesellschaft | Rotor disc with fluid removal channels to enhance life of spindle bolt |
US8973551B2 (en) | 2012-03-28 | 2015-03-10 | Cummins Inc. | Connecting rod lubrication apparatus |
US20160115996A1 (en) * | 2013-05-17 | 2016-04-28 | Voith Patent Gmbh | Tilting pad and radial plain bearing |
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US8075191B2 (en) * | 2009-09-28 | 2011-12-13 | Honeywell International Inc. | Helical inner diameter groove journal bearing |
CN105156463B (en) * | 2013-01-31 | 2018-12-14 | 三菱日立电力系统株式会社 | Tilting pad piece bearing arrangement |
DE102018211620A1 (en) * | 2018-07-12 | 2020-01-16 | Skf Marine Gmbh | bearings |
JP2020165533A (en) * | 2019-03-26 | 2020-10-08 | Ntn株式会社 | Fluid dynamic pressure bearing device |
JP7467303B2 (en) * | 2020-09-24 | 2024-04-15 | Ntn株式会社 | Fluid dynamic bearing device |
Citations (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4105267A (en) | 1976-03-19 | 1978-08-08 | Daido Metal Company, Ltd. | Bearing provided with oblique oil grooves and/or with a plurality of obliquely arranged rows of semicircular indentations |
US4459048A (en) | 1981-12-19 | 1984-07-10 | Mannesmann Aktiengesellschaft | Oil film bearing |
US4671676A (en) | 1985-09-03 | 1987-06-09 | Rockwell International Corporation | Hydrostatic bearing |
US4746230A (en) | 1984-02-17 | 1988-05-24 | Elliott Turbomachinery Co., Inc. | Tilt pad journal bearing |
US5007745A (en) | 1989-09-26 | 1991-04-16 | Delaware Capital Formation, Inc. | Low flow tilting pad thrust bearing |
US5054938A (en) | 1987-05-29 | 1991-10-08 | Ide Russell D | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5333955A (en) | 1993-01-11 | 1994-08-02 | Papa George M | Automotive main bearing |
US5516213A (en) | 1992-12-29 | 1996-05-14 | Oiles Corporation | Cylindrical bearing with solid lubricant embedded and fixed in inner peripheral surface thereof |
US5518321A (en) | 1994-04-21 | 1996-05-21 | Mitsubishi Jukogyo Kabushiki Kaisha | Tilting pad type bearing device |
US5558444A (en) | 1987-05-29 | 1996-09-24 | Ide; Russell D. | Bearings having spaced pads and methods of making the same |
US5660481A (en) | 1987-05-29 | 1997-08-26 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5702186A (en) | 1996-08-02 | 1997-12-30 | Westinghouse Electric Corporation | Journal bearing with leading edge groove vent |
US5743654A (en) | 1987-05-29 | 1998-04-28 | Kmc, Inc. | Hydrostatic and active control movable pad bearing |
US5772335A (en) | 1997-03-31 | 1998-06-30 | Whm Holding Company | Self-stabilizing, true-tilting pad with abruptly-stepped pocket for journal bearing |
US5951172A (en) | 1995-10-13 | 1999-09-14 | Orion Corporation | Sleeve bearing lubrication |
US6200034B1 (en) | 1997-03-31 | 2001-03-13 | Whm Holding Corporation | Self-stabilizing, true-tilting pad with generally tapered pocket for journal bearing |
US6491438B1 (en) | 1999-06-01 | 2002-12-10 | Daido Metal Company Ltd. | Main bearing for engine |
US6499883B2 (en) | 1997-03-31 | 2002-12-31 | Whm Holding Corporation | Tilting pad for bearings |
US20030190101A1 (en) | 2002-04-05 | 2003-10-09 | Sunonwealth Electric Machine Industry Co., Ltd. | Radially inner surface structure of a bearing |
US6739756B2 (en) | 2001-03-12 | 2004-05-25 | Whm Holding Corporation | Combination thrust bearing and journal bearing, and method for distributing fluid to same |
-
2005
- 2005-01-27 US US11/044,792 patent/US7165889B2/en not_active Expired - Fee Related
Patent Citations (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4105267A (en) | 1976-03-19 | 1978-08-08 | Daido Metal Company, Ltd. | Bearing provided with oblique oil grooves and/or with a plurality of obliquely arranged rows of semicircular indentations |
US4459048A (en) | 1981-12-19 | 1984-07-10 | Mannesmann Aktiengesellschaft | Oil film bearing |
US4746230A (en) | 1984-02-17 | 1988-05-24 | Elliott Turbomachinery Co., Inc. | Tilt pad journal bearing |
US4671676A (en) | 1985-09-03 | 1987-06-09 | Rockwell International Corporation | Hydrostatic bearing |
US5558444A (en) | 1987-05-29 | 1996-09-24 | Ide; Russell D. | Bearings having spaced pads and methods of making the same |
US5743654A (en) | 1987-05-29 | 1998-04-28 | Kmc, Inc. | Hydrostatic and active control movable pad bearing |
US5515458A (en) | 1987-05-29 | 1996-05-07 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5054938A (en) | 1987-05-29 | 1991-10-08 | Ide Russell D | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5660481A (en) | 1987-05-29 | 1997-08-26 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5007745A (en) | 1989-09-26 | 1991-04-16 | Delaware Capital Formation, Inc. | Low flow tilting pad thrust bearing |
US5516213A (en) | 1992-12-29 | 1996-05-14 | Oiles Corporation | Cylindrical bearing with solid lubricant embedded and fixed in inner peripheral surface thereof |
US5333955A (en) | 1993-01-11 | 1994-08-02 | Papa George M | Automotive main bearing |
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US5951172A (en) | 1995-10-13 | 1999-09-14 | Orion Corporation | Sleeve bearing lubrication |
US5702186A (en) | 1996-08-02 | 1997-12-30 | Westinghouse Electric Corporation | Journal bearing with leading edge groove vent |
US5772335A (en) | 1997-03-31 | 1998-06-30 | Whm Holding Company | Self-stabilizing, true-tilting pad with abruptly-stepped pocket for journal bearing |
US6079102A (en) | 1997-03-31 | 2000-06-27 | Whm Holdings Corporation | Journal bearing method employing self-stabilizing, true-tilting pad with abruptly-stepped pocket |
US6200034B1 (en) | 1997-03-31 | 2001-03-13 | Whm Holding Corporation | Self-stabilizing, true-tilting pad with generally tapered pocket for journal bearing |
US6499883B2 (en) | 1997-03-31 | 2002-12-31 | Whm Holding Corporation | Tilting pad for bearings |
US6491438B1 (en) | 1999-06-01 | 2002-12-10 | Daido Metal Company Ltd. | Main bearing for engine |
US6739756B2 (en) | 2001-03-12 | 2004-05-25 | Whm Holding Corporation | Combination thrust bearing and journal bearing, and method for distributing fluid to same |
US20030190101A1 (en) | 2002-04-05 | 2003-10-09 | Sunonwealth Electric Machine Industry Co., Ltd. | Radially inner surface structure of a bearing |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080107366A1 (en) * | 2006-11-06 | 2008-05-08 | Zippy Technology Corp. | Air fan bearing structure |
US20100054642A1 (en) * | 2008-08-26 | 2010-03-04 | Wolfgang Issler | Slide bearing |
US8322929B2 (en) * | 2008-08-26 | 2012-12-04 | Mahle International Gmbh | Slide bearing |
US20120017735A1 (en) * | 2010-07-22 | 2012-01-26 | Makita Corporation | Cutting tools having movable cover mounting structures |
US8608385B2 (en) | 2011-05-18 | 2013-12-17 | Federal-Mogul Corporation | Main bearing for engine with high belt load |
US8973551B2 (en) | 2012-03-28 | 2015-03-10 | Cummins Inc. | Connecting rod lubrication apparatus |
US9810257B2 (en) | 2012-03-28 | 2017-11-07 | Cummins Inc. | Connecting rod lubrication apparatus |
US10415630B2 (en) | 2012-03-28 | 2019-09-17 | Cummins Inc. | Connecting rod lubrication apparatus |
US20160115996A1 (en) * | 2013-05-17 | 2016-04-28 | Voith Patent Gmbh | Tilting pad and radial plain bearing |
US9689427B2 (en) * | 2013-05-17 | 2017-06-27 | Voith Patent Gmbh | Tilting pad and radial plain bearing |
US20140363307A1 (en) * | 2013-06-05 | 2014-12-11 | Siemens Aktiengesellschaft | Rotor disc with fluid removal channels to enhance life of spindle bolt |
US9951621B2 (en) * | 2013-06-05 | 2018-04-24 | Siemens Aktiengesellschaft | Rotor disc with fluid removal channels to enhance life of spindle bolt |
Also Published As
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US20060165326A1 (en) | 2006-07-27 |
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